Horizontal closed type compressor for vehicle use and cooling system of electric compressor for vehicle use

ABSTRACT

An object of the invention is to provide a horizontal closed type compressor for vehicle use which can suck a lubricating oil from an oil suction pipe without an oil surface of the lubricating oil becoming lower than the oil suction pipe, even in the case that a vehicle is inclined and the compressor is accordingly inclined. The horizontal closed type compressor for vehicle use is provided with a motor element provided within a closed container so as to direct a rotary shaft in a lateral direction, a compression element driven by the motor element, a lubricating oil received in the closed container, and an oil supplying means for feeding the lubricating oil to the compression element, the oil supplying means being provided in an opposite side to the motor element of the compression element, the compression element compresses the refrigerant gas sucked from an external portion of the closed container so as to discharge to the side of the motor element within the closed container, and thereafter discharges out of the closed container from the side of the oil supplying means, and partition walls sectioning an interior portion of the closed container while allowing the refrigerant gas and the lubricating oil to move are respectively provided in the side of the motor element and the side of the oil supplying means in the compression element.

BACKGROUND OF THE INVENTION

[0001] The present invention relates to a horizontal closed type compressor for vehicle use provided with an oil supplying means for feeding a lubricating oil received within a closed container to a compression element, and a cooling system of an electric compressor for vehicle use provided with a heat exchanging means arranged so as to exchange heat with an engine cooling system of a vehicle.

[0002] The horizontal closed type compressor is shown, for example, in Japanese Unexamined Patent Publication No. 7-229660 (F25B43/00). The horizontal closed type compressor of this kind is structured such that a motor element is provided within a wide closed container so as to direct a rotary shaft in a lateral direction, and a compression element (a rotary compressor, a scroll compressor or the like) driven by the motor element is provided. A lubricating oil is stored within the closed container, an oil suction pipe is provided in an opposite side to the motor element, and an oil pump is provided. Further, the lubricating oil inserted within the lubricating oil by the oil pump and sucked from the oil suction pipe circulates around a cylinder of the compression element and a bearing frame, thereby preventing the horizontal closed type compressor from being abraded.

[0003] On the contrary, in recent years, a car air-conditioner is mounted on most of the vehicles, however, the horizontal closed type compressor has been used in the car air-conditioner. However, in the case of using the horizontal closed type compressor in the vehicle, the horizontal closed type compressor for vehicle use is inclined in accordance that the vehicle is inclined while traveling along a mountain, a slope or the like, and the closed container is inclined so that a side of an oil pump (a side of the oil suction pipe) becomes high with respect to a side of the motor element. However, when the side of the oil pump becomes high, the lubricating oil stored within the closed container moves to the side of the motor element opposite to the side of the oil suction pipe due to a force of gravity. When the lubricating oil moves to the side opposite to the oil suction pipe, an oil surface of the lubricating oil becomes lower than the oil suction pipe, and the oil pump can not suck the lubricating oil from the oil suction pipe, whereby a lubricating performance is reduced. Accordingly, there has been desired a development of a horizontal closed type compressor for vehicle use which can suck the lubricating oil from the oil suction pipe without the oil surface of the lubricating oil becoming lower than the oil suction pipe, even in the case that the vehicle is inclined and the compressor is accordingly inclined.

[0004] Further, in recent years, the car air-conditioner is mounted on most of the vehicles, however, the car air-conditioner of this kind is structured such that a pipe in a discharge side of the compressor constituted by a rotary compressor, a scroll compressor or the like is connected to a radiator, and an outlet side of a condenser is connected to a liquid receiver. Further, a pipe in an outlet side of the liquid receiver is connected to a pressure reducing apparatus, and the pressure reducing apparatus is connected to the pipe in the suction side of the compressor via an evaporator (a cooling device) so as to constitute an annular refrigerant circuit.

[0005] Further, when the compressor is driven, a gas refrigerator having a high temperature and a high pressure and discharged from a compressor flows into the radiator, and the refrigerant radiates heat there so as to be condensed and liquefied. The condensed and liquefied liquid refrigerant flows into the liquid receiver so as to be stored, the liquid refrigerant once stored in the liquid receiver reaches the pressure reducing apparatus, is squeezed there and thereafter flows into the evaporator. The refrigerant flowing into the evaporator evaporates there, and absorbs heat from an environment at that time, thereby achieving a cooling effect. Further, in the refrigerant coming out of the evaporator, non-evaporated liquid refrigerant is separated into vapor and liquid and thereafter only the gas refrigerant is sucked to the compressor, and this circulation is repeated.

[0006] On the contrary, in the car air-conditioner mounted on the vehicle, with respect to the radiator of the rotary compressor, the scroll compressor or the like, a particular radiator is provided in an external portion of a passenger room such as an engine room or the like, and the radiator radiates heat in the gas refrigerant having a high temperature and a high pressure and discharged from the compressor so as to condense and liquefy.

[0007] However, with respect to the radiation of the gas refrigerant having a high temperature and a high pressure and discharged from the compressor, when the particular radiator is provided in the external portion of the passenger room such as the engine room or the like so as to condense and liquefy, there has been a problem that the engine room in a limited space becomes narrow.

[0008] Further, when placing the electric compressor in the engine room becoming a high temperature or the like, it is unavoidable that the temperature of the motor element, the lubricating oil or the like is increased, and there is a problem that a cooling capacity of the electric compressor for vehicle use is reduced.

SUMMARY OF THE INVENTION

[0009] The present invention is made for the purpose of solving the problems in the prior art mentioned above, and an object of the present invention is to provide a horizontal closed type compressor for vehicle use which can suck a lubricating oil from an oil suction pipe without an oil surface of the lubricating oil becoming lower than the oil suction pipe, even in the case that a vehicle is inclined and the compressor is accordingly inclined.

[0010] Another object of the present invention is to provide a cooling system of an electric compressor for vehicle use which can prevent a temperature of a motor element and a lubricating oil from being increased, and can efficiently use an engine room having a limited space.

[0011] That is, in accordance with the present invention, there is provided a horizontal closed type compressor for vehicle use comprising:

[0012] a motor element provided within a closed container so as to direct a rotary shaft in a lateral direction;

[0013] a compression element driven by the motor element;

[0014] a lubricating oil received in the closed container; and

[0015] an oil supplying means for feeding the lubricating oil to the compression element, the oil supplying means being provided in an opposite side to the motor element of the compression element,

[0016] wherein the compression element compresses the refrigerant gas sucked from an external portion of the closed container so as to discharge to the side of the motor element within the closed container, and thereafter discharges out of the closed container from the side of the oil supplying means, and partition walls sectioning an interior portion of the closed container while allowing the refrigerant gas and the lubricating oil to move are respectively provided in the side of the motor element and the side of the oil supplying means in the compression element.

[0017] In accordance with the present invention, since the structure is made such that the pressure in the side of the motor element within the closed container sectioned by the partition wall becomes higher than that in the side of the oil supplying means, for example, even in the case that the oil supplying means side of the compressor becomes high due to an incline of the vehicle, it is possible to prevent the lubricating oil stored in the side of the oil supplying means within the closed container from flowing out to the side of the motor element on the sake of the partition wall constituting a blocking layer. Accordingly, it is possible to restrict a reduction of the oil surface of the lubricating oil stored in the side of the oil supplying means within the closed container to the minimum, and it is possible to prevent a lubricating performance from being reduced. Accordingly, since a predetermined amount of lubricating oil can be stored in the side of the oil supplying means within the closed container even in the case that the horizontal closed type compressor is inclined, the oil supplying means can securely supply the lubricating oil sucked from the inner portion of the oil supplying means within the closed container to the cylinder and the bearing frame.

[0018] Further, in accordance with the present invention, there is provided a horizontal closed type compressor for vehicle use as recited in the aspect mentioned above, wherein an external pipe for discharging the refrigerant gas discharged from the compression element to the side of the motor element within the closed container via an external portion of the closed container is provided in the closed container.

[0019] In accordance with this structure, it is possible to radiate the high temperature refrigerant gas discharged from the compression element in a step passing through the external pipe so as to cool. Accordingly, for example, even in the case that a refrigerant such as a carbon dioxide as in the embodiment is used and the temperature of the horizontal closed type compressor is increased, it is possible to widely improve a cooling efficiency of the refrigerant discharged from the compressor.

[0020] Further, in accordance with the present invention, there is provided a horizontal closed type compressor for vehicle use as recited in each of the aspects mentioned above, wherein the compression element is constituted by a plurality of rotary compression elements provided between both of the partition walls.

[0021] In accordance with this structure, for example, it is possible to set the space between the partition walls so that the side of the motor element is high, the side of the oil supplying means is low and an intermediate pressure can be easily generated in a middle thereof. Accordingly, it is possible to easily store the lubricating oil in the side of the oil supplying means due to a pressure difference between the respective partition walls. Therefore, even in the case that the horizontal closed type compressor is inclined, it is possible to store a predetermined amount of lubricating oil in the oil storage portion, and the oil supplying means can securely supply the lubricating oil sucked from the inner portion of the oil storage portion to the cylinder and the bearing frame, whereby it is possible to widely improve a lubricating performance.

[0022] Further, in accordance with the present invention, there is provided a cooling system of an electric compressor for vehicle use comprising:

[0023] an electric compressor having a motor element provided within a closed container and a compression element driven by the motor element, and compressing a refrigerant gas sucked from an exterior portion of the closed container by the compression element and thereafter discharging to the external portion of the closed container; and

[0024] a heat exchanging means arranged so as to establish a heat exchanging relation with an engine cooling system of a vehicle, wherein the refrigerant gas discharged from the compression element is flowed to the heat exchanging means, is returned to the side of the motor element within the closed container and thereafter is discharged to the external portion of the closed container.

[0025] In accordance with this structure, the high temperature refrigerant gas discharged from the compression element can be radiated in a process of passing through the heat exchanging means arranged so as to establish the heat exchanging relation with the engine cooling system of the vehicle. Accordingly, since it is not necessary to provide a particular radiator, it is possible to efficiently use, for example, an engine room having a limited space.

[0026] In particular, for example, in the case of using a carbon dioxide corresponding to a natural refrigerant in the electric compressor, the refrigerant gas discharged from the compression element becomes high temperature on the basis of a property of the natural refrigerant, and the temperatures of the motor element and the lubricating oil are increased, however, since the high temperature refrigerant gas discharged from the compression element can be radiated in the step of communicating through the heat exchanging means, it is possible to prevent the temperatures of the motor element and the lubricating oil from being increased. Accordingly, even in the case that the electric compressor is placed in the engine room of the vehicle or the like which becomes high temperature, it is possible to prevent the temperatures of the motor element and the lubricating oil from being increased.

[0027] Further, in accordance with the present invention, there is provided a cooling system of an electric compressor for vehicle use as recited in the aspect mentioned above, wherein the heat exchanging means is arranged so as to establish a heat exchanging relation with a radiator of a vehicle.

[0028] In accordance with this structure, for example, it is possible to cool the high temperature refrigerant gas discharged from the electric compressor by the radiator for cooling the engine of the vehicle. Accordingly, it is possible to prevent a disadvantage that the compressor becomes high temperature so as to be burnt out.

BRIEF DESCRIPTION OF THE DRAWINGS

[0029]FIG. 1 is a vertical cross sectional side elevational view of a two-cylinder rotary compressor provided with first and second rotary compression elements corresponding to an embodiment of a horizontal closed type compressor for vehicle use in accordance with the present invention;

[0030]FIG. 2 is a vertical cross sectional side elevational view of a two-cylinder rotary compressor in which a side of an oil pump is inclined to be higher than a side of a motor element in the horizontal closed type compressor for vehicle use shown in FIG. 1;

[0031]FIG. 3 is a vertical cross sectional side elevational view of a two-cylinder rotary compressor in which the side of the motor element is inclined to be higher than the side of the oil pump in the horizontal closed type compressor for vehicle use shown in FIG. 1;

[0032]FIG. 4 is a vertical cross sectional side elevational view of a two-cylinder rotary compressor in accordance with another embodiment which is provided with first and second rotary compression elements corresponding to another embodiment of a horizontal closed type compressor for vehicle use;

[0033]FIG. 5 is a vertical cross sectional side elevational view of a two-cylinder rotary compressor in which a side of an oil pump is inclined to be higher than a side of a motor element in the horizontal closed type compressor for vehicle use shown in FIG. 4;

[0034]FIG. 6 is a vertical cross sectional side elevational view of a two-cylinder rotary compressor in which the side of the motor element is inclined to be higher than the side of the oil pump in the horizontal closed type compressor for vehicle use shown in FIG. 4;

[0035]FIG. 7 is a vertical cross sectional side elevational view of a one-cylinder rotary compressor which is provided with single rotary compression elements corresponding to another embodiment of a horizontal closed type compressor for vehicle use;

[0036]FIG. 8 is a vertical cross sectional side elevational view of a one-cylinder rotary compressor in which a side of an oil pump is inclined to be higher than a side of a motor element in the horizontal closed type compressor for vehicle use shown in FIG. 7;

[0037]FIG. 9 is a vertical cross sectional side elevational view of a one-cylinder rotary compressor in which the side of the motor element is inclined to be higher than the side of the oil pump in the horizontal closed type compressor for vehicle use shown in FIG. 7; and

[0038]FIG. 10 is a vertical cross sectional side elevational view of a two-cylinder rotary compressor which is provided with first and second rotary compression elements corresponding to an embodiment of a horizontal closed type compressor for vehicle use in accordance with an invention described in the fourth and fifth aspects.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

[0039] Next, a description will be given in detail of embodiments in accordance with the present invention with reference to the accompanying drawings.

[0040] A rotary compressor 1 in accordance with the present invention constitutes a refrigerant circuit of a car air-conditioner for air conditioning a passenger room of a motor vehicle (not shown), and is horizontally mounted, for example, within an engine room in the motor vehicle. The rotary compressor 1 is constituted by a cylindrical closed container 4 made of a steel plate, a motor element 6 arranged and received in an interior space of the closed container 4, and a compression element 8 comprising a first rotary compression element 2 and a second rotary compression element 3 which are driven by a rotary shaft 7 provided toward a horizontal direction of the motor element 6 (an axial direction of the closed container 4).

[0041] Further, a predetermined amount of carbon dioxide corresponding to an example of carbon dioxide gas is charged as a refrigerant within the closed container 4, and a predetermined amount of lubricating oil OL is received therewithin. Further, for example, a predetermined amount of polyalkylene glycol (PAG) is received as one example of the lubricating oil OL. In this case, the lubricating oil OL may be a poly alpha olein (PAO) or a mineral oil.

[0042] Further, in the embodiment, the closed container 4 is constituted by two members comprising a container main body 4A receiving the motor element 6 and the compression element 8, and a bowl-like end cap 4B closing an one end portion opening in a side of the motor element 6 of the container main body 4A, and a terminal (a wiring is omitted) 11 for supplying an electric power to the motor element 6 is provided in the end cap 4B. Further, an oil storage portion 12 for storing the lubricating oil is constructed within another end portion of the closed container 4 positioned in an opposite side to the motor element 6 of the compression element 8.

[0043] The motor element 6 is constituted by a stator 22 annularly mounted along an one end side inner peripheral surface of the container main body 4A in the closed container 4, and a rotor 24 arranged so as to be inserted to an inner side of the stator 22. The rotor 24 is fixed to the rotary shaft 7 extending to a horizontal direction through a center thereof.

[0044] The stator 22 has a stator core 26 obtained by laminating ring-like electromagnetic steel plates, and a stator coil 28 wound around the stator core 26. Further, the rotor 24 is also formed by a rotor core 30 made of an electromagnetic steel plate and a permanent magnet inserted to an inner portion thereof in the same manner as that of the stator 22, whereby a brushless DC motor is constituted by both elements.

[0045] An intermediate partition plate 36 is held between the first rotary compression element 2 and the second rotary compression element 3. That is, the first rotary compression element 2 and the second rotary compression element 3 are constituted by the intermediate partition plate 36, a cylinder 38 and a cylinder 40 arranged in left and right sides of the intermediate partition plate 36, left and right rollers 46 and 48 positioned within the left and right cylinders 38 and 40 and fitted to left and right eccentric portions 42 and 44 provided in the rotary shaft 7 with a phase difference of 180 degrees so as to eccentrically rotate, vanes (not shown) brought into contact with the left and right rollers 46 and 48 so as to respectively section inner portions of the left and right cylinders 38 and 40 into low pressure chamber sides and high pressure chamber sides, and a main frame (a left bearing) 51 and an auxiliary frame (a right bearing) 52 which close respective opening surfaces of the left and right cylinders 38 and 40 and also serving as a bearing of the rotary shaft 7.

[0046] A suction passage 53 is formed within the cylinder 38, and the suction passage 53 is communicated with a suction pipe 54 mounted to the closed container 4. The suction pipe 54 is connected to a cooler (not shown) for an artificial cooling provided within the passenger room. Further, a series of branch suction passages 56 communicated with the suction passage 53 are formed within the intermediate partition plate 36 and the cylinder 40. Further, a muffler cover 57 is mounted to the main frame 51, and a sound reduction chamber 58 suitably communicated with the inner portion of the cylinder 38 is formed within the muffler cover 57. Further, a muffler cover 59 is mounted to the auxiliary frame 52, and a sound reduction chamber 61 suitably communicated with the inner portion of the cylinder 40 is formed within the muffler cover 59.

[0047] Further, the sound reduction chamber 61 is communicated with the inner portion of the sound reduction chamber 58 by a communication passage 62 extending through the cylinders 38 and 40 and the intermediate partition plate 36, and the sound reduction chamber 58 is communicated with the inner portion of the closed container 4 in the side of the motor element 6 by a discharge port (not shown) formed in the muffler cover 57.

[0048] Further, an oil pump 66 corresponding to an oil supplying means is provided at an end portion in the side of the auxiliary frame 52 of the rotary shaft 7 (an opposite side to the motor element 6), an oil suction pipe 67 provided in the oil pump 66 is provided so as to drop down in a direction of the oil storage portion 12, and a lower end thereof is open in a lower portion of the oil storage portion 12. Further, a discharge pipe 71 is mounted to an upper portion of the closed container 4 in an opposite side to the motor element 6 of the compression element 8 (in a side of the oil storage portion 12 of the cylinder 40).

[0049] Further, partition walls 72 and 73 are provided in the side of the motor element 6 and the side of the oil storage portion 12 in the compression element 8. In this case, the partition wall 72 is mounted to the muffler cover 57 or the main frame 51 (or the cylinder 38 may be employed), and sections the inner portion of the closed container 4 into the side of the motor element 6 and the side of the compression element 8 while allowing a movement of the refrigerant gas and the lubricating oil. Further, the partition wall 73 is mounted to the cylinder 40 (or the auxiliary frame 52 or the muffler cover 59 may be employed), and sections the inner portion of the closed container 4 into the side of the compression element 8 and the side of the oil storage portion 12 while allowing the movement of the refrigerant gas and the lubricating oil. Further, the discharge pipe 71 is positioned in the side of the oil storage portion 12 of the partition wall 73.

[0050] In the structure mentioned above, when an electric current is applied to a coil 28 of the motor element 6 via the terminal 11 and a wiring (not shown), the rotor 24 rotates. On the basis of the rotation, the left and right rollers 46 and 48 fitted to the left and right eccentric portions 42 and 44 integrally provided with the rotary shaft 7 eccentrically rotate within the left and right cylinders 38 and 40.

[0051] Accordingly, the refrigerant gas sucked into the suction pipe 54 from the external portion is sucked into the side of the low pressure chamber of the cylinder 38 via the suction passage 53, and sucked into the side of the lower pressure chamber of the cylinder 40 via the branch suction passage 56. The sucked low pressure refrigerant gas is compressed in accordance with operations of the roller 46, the roller 48 and the vane, respectively so as to become high temperature and high pressure and reach the sound reduction chamber 58 from the side of the high pressure chamber of the cylinder 38, thereby being discharged within the closed container 4 in the side of the motor element 6 from the discharge port. Further, the refrigerant gas reaches the sound reduction chamber 58 from the side of the high pressure chamber of the cylinder 40 via the sound reduction chamber 61 and the communication passage 62 so as to be discharged within the closed container 4 in the side of the motor element 6 from the discharge port.

[0052] As mentioned above, the refrigerant gas having a high temperature and a high pressure and discharged into the side of the motor element 6 within the closed container 4 reaches the side of the oil storage portion 12 within the closed container 4 through the gap formed between the respective cylinders 38 and 40 of the compression element 8 and the partition wall 73 so as to be discharged into the external portion from the discharge pipe 71.

[0053] Accordingly, a pressure distribution within the closed container 4 is made so that the side of the motor element 6 in the partition wall 72 has a highest high pressure HH, the intermediate partition plate 36 portion of the compression element 8 between the partition walls 72 and 73 has a middle high pressure HM lower than the above, and the side of the oil storage portion 12 of the partition wall 73 in the discharge pipe 71 has a lowest high pressure HL.

[0054] On the contrary, the oil pump 66 is rotated due to a rotation of the rotary shaft 7 so as to suck the lubricating oil within the oil storage portion 12 from the lower end opening of the oil suction pipe 67. Further, the lubricating oil is supplied to the sliding portions within the respective cylinders 38 and 40 and the sliding portions between the respective frames 51 and 52 and the rotary shaft 7 through the rotary shaft 7 so as to lubricate them.

[0055] As mentioned above, in the lubricating oil stored in the oil storage portion 12, since the pressure distribution within the closed container 4 is made so that the side of the motor element 6 in the partition wall 72 has the higher high pressure HH, the partition walls 72 and 73 have the middle high pressure HM, and the side of the oil storage portion 12 of the partition wall 73 has the lower high pressure HL, the lubricating oil within the closed container 4 can be held in the oil storage portion 12 (the side of the oil pump 6) due to the higher high pressure HH, the middle high pressure HM and the lower high pressure HL. Accordingly, the lubricating oil stored in the oil storage portion 12 can be prevented from flowing out to the side of the motor element 6 by both of the partition walls 73 and 72. Therefore, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinders 38 and 40 and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing)52 serving as the bearing of the rotary shaft 7.

[0056] In this case, a description will be given of a two-cylinder rotary compressor in which the side of the oil pump 66 is inclined to be higher than the side of the motor element 6 in the horizontal closed type compressor 1 for vehicle use with reference to FIG. 2. In this case, the closed container 4 is inclined at an angle (about 30.0 degrees) being higher in the side of the oil pump 66 and lower in the side of the motor element 6. In the case of making the side of the oil pump 66 in the closed container 4 higher as mentioned above, the lubricating oil stored in the oil storage portion 12 of the partition wall 73 having the discharge pipe 71 is going to move to the side of the motor element 6 through the gap formed among the partition wall 73, the respective cylinders 38 and 40 and the partition wall 72 due to the gravitational force, however, since the pressure distribution of the high pressure refrigerant discharged within the closed container 4 is structured such that the side of the motor element 6 in the partition wall 72 has the higher high pressure HH, the partition walls 72 and 73 has the middle high pressure HM, and the side of the oil storage portion 12 in the partition wall 73 has the lower high pressure HL, the lubricating oil stored in the oil storage portion 12 can be prevented from flowing out to the side of the motor element 6 due to the pressure difference generated by both of the partition walls 73 and 72.

[0057] Accordingly, even in the case that the horizontal closed type compressor mounted on the vehicle is inclined so that the side of the oil pump 66 becomes higher than the side of the motor element 6 (the opposite side to the oil pump 66), it is possible to restrict the reduction of the oil surface of the lubricating oil stored in the side of the oil pump 66 within the closed container 4 to the minimum, it is possible to prevent a lubricating performance from being lowered, and it is possible to store a predetermined amount of lubricating oil in the oil storage portion 12. That is, even in the case that the side of the oil pump 66 in the closed container 4 is inclined to become higher, it is possible to store a small amount of lubricating oil in the side of the motor element 6 in the partition wall 72 having the higher high pressure HH and store most of the lubricating oil in the oil storage portion 12 (the side of the oil pump 66) corresponding to the right side of the partition wall 73 having the lower high pressure HL. Accordingly, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinders 38 and 40 and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing) 52 serving as the bearing of the rotary shaft 7.

[0058] Next, a description will be given of a two-cylinder rotary compressor 1 in which the side of the motor element 6 is inclined to be higher than the side of the oil pump 66 in the horizontal closed type compressor for vehicle use with reference to FIG. 3. In this case, the closed container 4 is inclined at an angle (about 30.0 degrees) being lower in the side of the oil pump 66 and higher in the side of the motor element 6. In the case of making the side of the motor element 6 higher than the side of the oil pump 66 in the closed container 4 as mentioned above, the side of the oil pump 66 becomes lower, and the lubricating oil stored in the oil storage portion 12 of the partition wall 73 having the discharge pipe 71 is stored within the oil storage portion 12 without flowing out to the side of the motor element 6 due to the gravitational force.

[0059] Accordingly, in the case that the horizontal closed type compressor mounted on the vehicle is inclined so that the side of the motor element 6 becomes higher than the side of the oil pump 66, it is possible to store a predetermined amount of lubricating oil in the oil storage portion 12. Accordingly, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinders 38 and 40, and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing) 52 serving as the bearing of the rotary shaft 7.

[0060] Next, FIG. 4 shows a two-cylinder rotary compressor in accordance with another embodiment which is provided with the first and second rotary compression elements 2 and 3 corresponding to an embodiment of the horizontal closed type compressor for vehicle use. In this horizontal closed type compressor for vehicle use, an external pipe 64 for discharging the refrigerant gas having high temperature and high pressure and discharged from the compression element 8 to the side of the motor element 6 within the closed container 4 via the external portion of the closed container 4 is provided. That is, the horizontal closed type compressor for vehicle use is structured such that on the basis of the rotary compressor 1 mentioned above, the external pipe 64 is connected to a discharge port (not shown) formed in the muffler cover 57. The external pipe 64 temporarily goes out to the external portion of the closed container 4 from the discharge port and is communicated with the inner portion of the closed container 4 (the side of the motor element 6) from the side of the terminal 11 of the closed container 4.

[0061] Further, the oil pump 66 is provided in the end portion in the side of the auxiliary frame 52 (the opposite side to the motor element 6) of the rotary shaft 7 in the same manner as mentioned above, the oil suction pipe 67 provided in the oil pump 66 drops down in the direction of the oil storage portion 12, and the lower end of the oil suction pipe 67 is open in the lower portion of the oil storage portion 12. Further, the discharge pipe 71 is mounted to the upper portion of the closed container 4 in the opposite side to the motor element 6 of the compression element 8 (in the side of the oil storage portion 12 of the cylinder 40). The other structures are the same as those of the rotary compressor 1 mentioned above.

[0062] In accordance with the structure mentioned above, when the electric current is applied to the coil 28 of the motor element 6 via the terminal 11 and a wiring (not shown), the rotor 24 rotates. Due to the rotation, the left and right rollers 46 and 48 fitted to the left and right eccentric portions 42 and 44 integrally provided with the rotary shaft 7 eccentrically rotate within the left and right cylinders 38 and 40.

[0063] Accordingly, the refrigerant gas sucked into the suction pipe 54 from the external portion is sucked into the side of the low pressure chamber of the cylinder 38 via the suction passage 53, and sucked into the side of the lower pressure chamber of the cylinder 40 via the branch suction passage 56. The sucked low pressure refrigerant gas is compressed in accordance with operations of the roller 46, the roller 48 and the vane, respectively so as to become high temperature and high pressure and reach the sound reduction chamber 58 from the side of the high pressure chamber of the cylinder 38, thereby being discharged within the external pipe 64 from the discharge port. Further, the refrigerant gas reaches the sound reduction chamber 58 from the side of the high pressure chamber of the cylinder 40 via the sound reduction chamber 61 and the communication passage 62 so as to be discharged within the external pipe 64 from the discharge port.

[0064] Further, the refrigerant gas having a high temperature and a high pressure and discharged within the external pipe 64 from the discharge port is discharged within the closed container 4 (the side of the motor element 6) after being heat exchanged with the ambient air within the external pipe 64 provided outside the closed container 4 so as to be cooled. The refrigerant gas having a high temperature and a high pressure and cooled so as to be discharged within the closed container 4 reaches the side of the oil storage portion 12 within the closed container 4 while cooling the motor element 6 of the closed container 4 or the respective cylinders 38 and 40 or the like becoming high temperature, in the step of passing through the gap formed among the closed container 4, the partition wall 72, the respective cylinders 38 and 40 of the compression element 8 and the partition wall 73 so as to be discharged into the external portion from the discharge pipe 71.

[0065] Accordingly, a pressure distribution within the closed container 4 is made so that the side of the motor element 6 in the partition wall 72 has a highest high pressure HH, the intermediate partition plate 36 portion of the compression element 8 between the partition walls 72 and 73 has a middle high pressure HM lower than the above, and the side of the oil storage portion 12 of the partition wall 73 in the discharge pipe 71 has a lowest high pressure HL.

[0066] On the contrary, the oil pump 66 is rotated due to a rotation of the rotary shaft 7 so as to suck the lubricating oil within the oil storage portion 12 from the lower end opening of the oil suction pipe 67. Further, the lubricating oil is supplied to the sliding portions within the respective cylinders 38 and 40 and the sliding portions between the respective frames 51 and 52 and the rotary shaft 7 through the rotary shaft 7 so as to lubricate them.

[0067] As mentioned above, in the lubricating oil stored in the oil storage portion 12, since the pressure distribution within the closed container 4 is made so that the side of the motor element 6 in the partition wall 72 has the higher high pressure HH, the partition walls 72 and 73 have the middle high pressure HM, and the side of the oil storage portion 12 of the partition wall 73 has the lower high pressure HL, the lubricating oil can be held in the oil storage portion 12 (the side of the oil pump 6) due to the higher high pressure HH, the middle high pressure HM and the lower high pressure HL, in the same manner as mentioned above. Accordingly, the lubricating oil stored in the oil storage portion 12 can be prevented from flowing out to the side of the motor element 6 by the partition walls 73 and 72. Therefore, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinders 38 and 40 and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing)52 serving as the bearing of the rotary shaft 7 while preventing the rotary compressor 1 from being heated.

[0068] In this case, a description will be given of a two-cylinder rotary compressor in which the side of the oil pump 66 is inclined to be higher than the side of the motor element 6 in the horizontal closed type compressor 1 for vehicle use with reference to FIG. 5. In this case, the closed container 4 is inclined at an angle (about 30.0 degrees) being higher in the side of the oil pump 66 and lower in the side of the motor element 6. In the case of making the side of the oil pump 66 in the closed container 4 higher as mentioned above, the lubricating oil stored in the oil storage portion 12 of the partition wall 73 having the discharge pipe 71 is going to move to the side of the motor element 6 through the gap formed among the partition wall 73, the respective cylinders 38 and 40 and the partition wall 72 due to the gravitational force, however, since the pressure distribution within the closed container 4 is structured such that the side of the motor element 6 in the partition wall 72 has the higher high pressure HH, the partition walls 72 and 73 has the middle high pressure HM, and the side of the oil storage portion 12 in the partition wall 73 has the lower high pressure HL while cooling the motor element 6 of the closed container 4 or the respective cylinders 38 and 40 or the like becoming high temperature by the high pressure refrigerant cooled within the external pipe 64, the lubricating oil stored in the oil storage portion 12 can be prevented from flowing out to the side of the motor element 6 due to the pressure difference within the closed container 4 generated by both of the partition walls 73 and 72 while preventing the rotary compressor 1 from being heated. That is, even in the case that the side of the oil pump 66 in the closed container 4 is inclined to be higher, it is possible to store a small amount of lubricating oil in the side of the motor element 6 in the partition wall 72 having the higher high pressure HH and store most of the lubricating oil in the oil storage portion 12 (the side of the oil pump 66) corresponding to the right side of the partition wall 73 having the lower high pressure HL.

[0069] Accordingly, even in the case that the temperature of the rotary compressor 1 using the carbon dioxide for the refrigerant is increased, it is possible to improve a cooling efficiency of the refrigerant discharged from the compressor, and even in the case that the horizontal closed type compressor mounted on the vehicle is inclined so that the side of the oil pump 66 becomes higher, it is possible to restrict the reduction of the oil surface of the lubricating oil stored in the side of the oil pump 66 within the closed container 4 to the minimum, it is possible to prevent the lubricating performance from being reduced, and it is possible to store a predetermined amount of lubricating oil in the oil storage portion 12. Therefore, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinders 38 and 40 and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing) 52 serving as the bearing of the rotary shaft 7 while preventing the rotary compressor 1 from being heated.

[0070] Next, a description will be given of a two-cylinder rotary compressor 1 in which the side of the motor element 6 is inclined to be higher than the side of the oil pump 66 in the horizontal closed type compressor for vehicle use with reference to FIG. 6. In this case, the closed container 4 is inclined at an angle (about 30.0 degrees) being lower in the side of the oil pump 66 and higher in the side of the motor element 6. In the case of making the side of the motor element 6 higher in the closed container 4 as mentioned above, the side of the oil pump 66 becomes lower, and the lubricating oil stored in the oil storage portion 12 of the partition wall 73 having the discharge pipe 71 is stored within the oil storage portion 12 without flowing out to the side of the motor element 6 due to the gravitational force. Further, since the pressure distribution within the closed container 4 is structured such that the side of the motor element 6 in the partition wall 72 has the higher high pressure, the partition walls 72 and 73 have the middle high pressure HM and the side of the oil storage portion 12 in the partition wall 73 has the lower high pressure HL, the lubricating oil stored in the oil storage portion 12 is prevented from further flowing out to the side of the motor element 6 by the partition walls 73 and 72.

[0071] Accordingly, even in the case that the horizontal closed type compressor mounted on the vehicle is inclined so that the side of the motor element 6 becomes higher, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinders 38 and 40, and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing) 52 serving as the bearing of the rotary shaft 7 while preventing the rotary compressor 1 from being heated.

[0072] Next, FIG. 7 shows a single-cylinder rotary compressor 80 provided with a single rotary compression element 81 corresponding to an embodiment of the horizontal closed type compressor for vehicle use. In this case, the rotary compression element of the horizontal closed type compressor for vehicle use is constituted by a rotary compressor having one cylinder, constitutes a refrigerant circuit of a car air-conditioner for air conditioning a passenger room of a motor vehicle (not shown) in the same manner as that mentioned above, and is horizontally mounted, for example, within an engine room in the motor vehicle. The rotary compressor 80 is also constituted by a cylindrical closed container 4 made of a steel plate, a motor element 6 arranged and received in an interior space of the closed container 4, and a compression element 8 comprising the rotary compression element 81 which is driven by a rotary shaft 7 provided toward a horizontal direction of the motor element 6 (an axial direction of the closed container 4).

[0073] Further, a predetermined amount of carbon dioxide corresponding to an example of carbon dioxide gas is charged as a refrigerant within the closed container 4, and a predetermined amount of lubricating oil OL is received therewithin. Further, for example, a predetermined amount of polyalkylene glycol (PAG) is received as one example of the lubricating oil OL. In this case, the lubricating oil OL may be a poly alpha olein (PAO) or a mineral oil.

[0074] Further, in the embodiment, the closed container 4 is constituted by two members comprising a container main body 4A receiving the motor element 6 and the compression element 8, and a bowl-like end cap 4B closing an one end portion opening in a side of the motor element 6 of the container main body 4A, and a terminal (a wiring is omitted) 11 for supplying an electric power to the motor element 6 is provided in the end cap 4B. Further, an oil storage portion 12 for storing the lubricating oil is constructed within another end portion of the closed container 4 positioned in an opposite side to the motor element 6 of the compression element 8.

[0075] The motor element 6 is constituted by a stator 22 annularly mounted along an one end side inner peripheral surface of the container main body 4A in the closed container 4, and a rotor 24 arranged so as to be inserted to an inner side of the stator 22. The rotor 24 is fixed to the rotary shaft 7 extending to a horizontal direction through a center thereof.

[0076] The stator 22 has a stator core 26 obtained by laminating ring-like electromagnetic steel plates, and a stator coil 28 wound around the stator core 26. Further, the rotor 24 is also formed by a rotor core 30 made of an electromagnetic steel plate and a permanent magnet inserted to an inner portion thereof in the same manner as that of the stator 22, whereby a brushless DC motor is constituted by both elements.

[0077] The rotary compression element 81 is constituted by a roller 46 positioned within the cylinder 38 and fitted to the eccentric portion 42 provided in the rotary shaft 7 so as to eccentrically rotate, a vane (not shown) brought into contact with the roller 46 so as to section the inner portion of the cylinder 38 into a low pressure chamber side and a high pressure chamber side, and a main frame (a left bearing) 51 and an auxiliary frame (a right bearing) 52 which closes an opening surface of the cylinder 38 and also serving as a bearing of the rotary shaft 7.

[0078] A suction passage 53 is formed within the cylinder 38, and the suction passage 53 is communicated with a suction pipe 54 mounted to the closed container 4. Further, a muffler cover 57 is mounted to the main frame 51, and a sound reduction chamber 58 suitably communicated with the inner portion of the cylinder 38 is formed within the muffler cover 57. Further, a muffler cover 59 is mounted to the auxiliary frame 52, and a sound reduction chamber 61 suitably communicated with the sound reduction chamber 58 is formed within the muffler cover 59.

[0079] Further, the sound reduction chamber 58 is provided with a discharge port (not shown) formed in the muffler cover 57, and an external pipe 64 is connected to the discharge port. The external pipe 64 temporarily goes out of the closed container 4 from the discharge port and is communicated with the inner portion of the closed container 4 (in the side of the motor element 6) from the side of the terminal 11 of the closed container 4.

[0080] Further, in the same manner as mentioned above, an oil pump 66 corresponding to an oil supplying means is provided at an end portion in the side of the auxiliary frame 52 of the rotary shaft 7 (an opposite side to the motor element 6), an oil suction pipe 67 provided in the oil pump 66 drops down in a direction of the oil storage portion 12, and a lower end of the oil suction pipe 67 is open in a lower portion of the oil storage portion 12. Further, a discharge pipe 71 is mounted to an upper portion of the closed container 4 in an opposite side to the motor element 6 of the compression element 8 (in a side of the oil storage portion 12 of the cylinder 38).

[0081] Further, partition walls 72 and 73 are provided in the side of the motor element 6 and the side of the oil storage portion 12 in the compression element 8, in the same manner as mentioned above. In this case, the partition wall 72 is mounted to the muffler cover 57 or the main frame 51 (or the cylinder 38 may be employed), and sections the inner portion of the closed container 4 into the side of the motor element 6 and the side of the compression element 8 while allowing a movement of the refrigerant gas and the lubricating oil. Further, the partition wall 73 is mounted to the cylinder 38 (or the auxiliary frame 52 or the muffler cover 59 may be employed), and sections the inner portion of the closed container 4 into the side of the compression element 8 and the side of the oil storage portion 12 while allowing the movement of the refrigerant gas and the lubricating oil. Further, the discharge pipe 71 is positioned in the side of the oil storage portion 12 of the partition wall 73.

[0082] In the structure mentioned above, when an electric current is applied to a coil 28 of the motor element 6 via the terminal 11 and a wiring (not shown), the rotor 24 rotates. On the basis of the rotation, the roller 46 fitted to the eccentric portion 42 integrally provided with the rotary shaft 7 eccentrically rotate within the cylinder 38. Accordingly, the refrigerant gas sucked into the suction pipe 54 from the external portion is sucked into the side of the low pressure chamber of the cylinder 38 via the suction passage 53.

[0083] Further, the sucked low pressure refrigerant gas is compressed in accordance with operations of the roller 46 and the vane so as to become high temperature and high pressure and reach the sound reduction chamber 58 from the side of the high pressure chamber of the cylinder 38, thereby being discharged within the external pipe 64 from the discharge port. The refrigerant gas having a high temperature and a high pressure and discharged within the external pipe 64 from the discharge port is discharged within the closed container 4 after being heat exchanged with the ambient air within the external pipe 64 provided outside the closed container 4 so as to be cooled. The cooled high pressure refrigerant gas reaches the side of the oil storage portion 12 within the closed container 4 while cooling the motor element 6 of the closed container 4 or the respective cylinder 38 or the like becoming high temperature, in the step of passing through the gap formed among the closed container 4, the partition wall 72, the cylinder 38 of the compression element 8 and the partition wall 73 so as to be discharged into the external portion from the discharge pipe 71.

[0084] Accordingly, a pressure distribution within the closed container 4 is made so that the side of the motor element 6 in the partition wall 72 has a highest high pressure HH, the compression element 8 portion between the partition walls 72 and 73 has a middle high pressure HM lower than the above, and the side of the oil storage portion 12 of the partition wall 73 in the discharge pipe 71 has a lowest high pressure HL, in the same manner as that mentioned above.

[0085] On the contrary, the oil pump 66 is rotated due to a rotation of the rotary shaft 7 so as to suck the lubricating oil within the oil storage portion 12 from the lower end opening of the oil suction pipe 67. Further, the lubricating oil is supplied to the sliding portions within the cylinder 38 and the sliding portions between the respective frames 51 and 52 and the rotary shaft 7 through the rotary shaft 7 so as to lubricate them.

[0086] As mentioned above, in the lubricating oil stored in the oil storage portion 12, since the pressure distribution within the closed container 4 is made so that the side of the motor element 6 in the partition wall 72 has the higher high pressure HH, the partition walls 72 and 73 have the middle high pressure HM, and the side of the oil storage portion 12 of the partition wall 73 has the lower high pressure HL, the lubricating oil can be held in the oil storage portion 12 (the side of the oil pump 6) due to the pressure difference among the higher high pressure HH, the middle high pressure HM and the lower high pressure HL which are generated by both of the partition walls 72 and 73, in the same manner as mentioned above. Accordingly, the lubricating oil stored in the oil storage portion 12 can be prevented from flowing out to the side of the motor element 6 by the partition walls 73 and 72. Therefore, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinder 38 and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing)52 serving as the bearing of the rotary shaft 7 while preventing the rotary compressor 80 from being heated.

[0087] In this case, a description will be given of a two-cylinder rotary compressor in which the side of the oil pump 66 is inclined to be higher than the side of the motor element 6 in the horizontal closed type compressor 1 for vehicle use with reference to FIG. 8. In this case, the closed container 4 is inclined at an angle (about 30.0 degrees) being higher in the side of the oil pump 66 and lower in the side of the motor element 6. In the case of making the side of the oil pump 66 in the closed container 4 higher as mentioned above, the lubricating oil stored in the oil storage portion 12 of the partition wall 73 having the discharge pipe 71 is going to move to the side of the motor element 6 through the gap formed among the partition wall 73, the cylinder 38 and the partition wall 72 due to the gravitational force, however, since the pressure distribution within the closed container 4 is structured such that the side of the motor element 6 in the partition wall 72 has the higher high pressure HH, the partition walls 72 and 73 has the middle high pressure HM, and the side of the oil storage portion 12 in the partition wall 73 has the lower high pressure HL while cooling the motor element 6 of the closed container 4 or the cylinder 38 or the like becoming high temperature by the high pressure refrigerant cooled within the external pipe 64, the lubricating oil stored in the oil storage portion 12 can be prevented from flowing out to the side of the motor element 6 due to the pressure difference generated by both of the partition walls 73 and 72 while preventing the rotary compressor 80 from being heated. That is, even in the case that the side of the oil pump 66 in the closed container 4 is inclined to be higher, it is possible to store a small amount of lubricating oil in the side of the motor element 6 in the partition wall 72 having the higher high pressure HH and store most of the lubricating oil in the oil storage portion 12 (the side of the oil pump 66) corresponding to the right side of the partition wall 73 having the lower high pressure HL.

[0088] Accordingly, even in the case that the temperature of the rotary compressor 80 using the carbon dioxide for the refrigerant is increased, it is possible to improve a cooling efficiency of the refrigerant discharged from the compressor, and even in the case that the horizontal closed type compressor mounted on the vehicle is inclined so that the side of the oil pump 66 becomes higher, it is possible to restrict the reduction of the oil surface of the lubricating oil stored in the side of the oil pump 66 within the closed container 4 to the minimum, it is possible to prevent the lubricating performance from being reduced, and it is possible to store a predetermined amount of lubricating oil in the oil storage portion 12. Therefore, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinder 38 and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing) 52 serving as the bearing of the rotary shaft 7 while preventing the rotary compressor 80 from being heated.

[0089] Next, a description will be given of a two-cylinder rotary compressor 1 in which the side of the motor element 6 is inclined to be higher than the side of the oil pump 66 in the horizontal closed type compressor for vehicle use with reference to FIG. 9. In this case, the closed container 4 is inclined at an angle (about 30.0 degrees) being lower in the side of the oil pump 66 and higher in the side of the motor element 6. In the case of making the side of the motor element 6 higher in the closed container 4 as mentioned above, the side of the oil pump 66 becomes lower, and the lubricating oil stored in the oil storage portion 12 of the partition wall 73 having the discharge pipe 71 is stored within the oil storage portion 12 without flowing out to the side of the motor element 6 due to the gravitational force. Further, since the pressure distribution within the closed container 4 is structured such that the side of the motor element 6 in the partition wall 72 has the higher high pressure, the partition walls 72 and 73 have the middle high pressure HM and the side of the oil storage portion 12 in the partition wall 73 has the lower high pressure HL, the lubricating oil stored in the oil storage portion 12 is prevented from flowing out to the side of the motor element 6 due to the pressure difference between both of the partition walls 73 and 72.

[0090] Accordingly, even in the case that the horizontal closed type compressor mounted on the vehicle is inclined so that the side of the motor element 6 becomes higher, the oil pump 66 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinder 38, and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing) 52 serving as the bearing of the rotary shaft 7 while preventing the rotary compressor 80 from being heated.

[0091] In this case, in the embodiment mentioned above, the rotary compressor is employed as one embodiment of the closed type compressor, however, the structure is not limited to this, and the present invention can be effectively applied to a closed type scroll compressor comprising a pair of scrolls engaging with each other.

[0092] As described in detail above, in accordance with the present invention, the horizontal closed type compressor for vehicle use is provided with the motor element provided within the closed container so as to direct the rotary shaft in the lateral direction, the compression element driven by the motor element, the lubricating oil received in the closed container, and the oil supplying means for feeding the lubricating oil to the compression element, the oil supplying means being provided in the opposite side to the motor element of the compression element, and the compression element compresses the refrigerant gas sucked from the external portion of the closed container so as to discharge to the side of the motor element within the closed container, and thereafter discharges out of the closed container from the side of the oil supplying means, and the partition walls sectioning the interior portion of the closed container while allowing the refrigerant gas and the lubricating oil to move are respectively provided in the side of the motor element and the side of the oil supplying means in the compression element. Accordingly, since the structure is made such that the pressure in the side of the motor element within the closed container sectioned by the partition wall becomes higher than that in the side of the oil supplying means, for example, even in the case that the oil supplying means side of the horizontal closed type compressor becomes high due to the incline of the vehicle, it is possible to prevent the lubricating oil stored in the side of the oil supplying means within the closed container from flowing out to the side of the motor element on the sake of the partition wall constituting the blocking layer. Accordingly, it is possible to restrict the reduction of the oil surface of the lubricating oil stored in the side of the oil supplying means within the closed container to the minimum, and it is possible to prevent a lubricating performance from being reduced. Accordingly, since a predetermined amount of lubricating oil can be stored in the side of the oil supplying means within the closed container even in the case that the horizontal closed type compressor is inclined so as to be high in the side of the oil supplying means, the oil supplying means can securely supply the lubricating oil sucked from the inner portion of the oil supplying means within the closed container to the cylinder and the bearing frame.

[0093] Further, since the horizontal closed type compressor for vehicle use in accordance with the present invention is provided, in addition to the structure mentioned above, with the external pipe for discharging the refrigerant gas discharged from the compression element to the side of the motor element within the closed container via the external portion of the closed container in the closed container, it is possible to radiate the high temperature refrigerant gas discharged from the compression element in the step passing through the external pipe so as to cool. Accordingly, for example, even in the case that the refrigerant such as a carbon dioxide as in the embodiment is used and the temperature of the horizontal closed type compressor is increased, it is possible to widely improve the cooling efficiency of the refrigerant discharged from the compressor.

[0094] Further, since the horizontal closed type compressor for vehicle use in accordance with the present invention is structured, in addition to the structure described in the first aspect of the second aspect, such that the compression element is constituted by a plurality of rotary compression elements provided between both of the partition walls, for example, it is possible to set the space between the partition walls so that the side of the motor element is high, the side of the oil supplying means is low and the intermediate pressure can be easily generated in a middle thereof. Accordingly, it is possible to easily store the lubricating oil in the side of the oil supplying means due to a pressure difference between the respective partition walls. Therefore, even in the case that the horizontal closed type compressor is inclined so as to be high in the side of the oil supplying means, it is possible to store the predetermined amount of lubricating oil in the oil storage portion, and the oil supplying means can securely supply the lubricating oil sucked from the inner portion of the oil storage portion to the cylinder and the bearing frame, whereby it is possible to widely improve the lubricating performance.

[0095] Next, a description will be given in detail of an embodiment in accordance with the invention described in the fourth aspect and the fifth aspect with reference to FIG. 10.

[0096] A rotary compressor 101 of a cooling system in an electric compressor for vehicle use in accordance with the present invention constitutes a refrigerant circuit of a car air-conditioner for air conditioning a passenger room of a motor vehicle (not shown), and is horizontally mounted, for example, within an engine room in the motor vehicle. The rotary compressor 101 is constituted by a cylindrical closed container 104 made of a steel plate, a motor element 106 arranged and received in an interior space of the closed container 104, and a compression element 108 comprising a first rotary compression element 102 and a second rotary compression element 103 which are driven by a rotary shaft 107 provided toward a horizontal direction of the motor element 106 (an axial direction of the closed container 104).

[0097] Further, a predetermined amount of carbon dioxide corresponding to an example of carbon dioxide gas is charged as a refrigerant within the closed container 104, and a predetermined amount of lubricating oil OL is received therewithin. Further, for example, a predetermined amount of polyalkylene glycol (PAG) is received as one example of the lubricating oil OL. In this case, the lubricating oil OL may be a poly alpha olein (PAO) or a mineral oil.

[0098] Further, in the embodiment, the closed container 104 is constituted by two members comprising a container main body 104A receiving the motor element 106 and the compression element 108, and a bowl-like end cap 104B closing an one end portion opening in a side of the motor element 106 of the container main body 104A, and a terminal (a wiring is omitted) 111 for supplying an electric power to the motor element 106 is provided in the end cap 104B. Further, an oil storage portion 112 for storing the lubricating oil is constructed within another end portion of the closed container 104 positioned in an opposite side to the motor element 106 of the compression element 108.

[0099] The motor element 106 is constituted by a stator 122 annularly mounted along an one end side inner peripheral surface of the container main body 104A in the closed container 104, and a rotor 124 arranged so as to be inserted to an inner side of the stator 122. The rotor 124 is fixed to the rotary shaft 107 extending to a horizontal direction through a center thereof.

[0100] The stator 122 has a stator core 126 obtained by laminating ring-like electromagnetic steel plates, and a stator coil 128 wound around the stator core 126. Further, the rotor 124 is also formed by a rotor core 130 made of an electromagnetic steel plate and a permanent magnet inserted to an inner portion thereof in the same manner as that of the stator 122, whereby a brushless DC motor is constituted by both elements.

[0101] An intermediate partition plate 136 is held between the first rotary compression element 102 and the second rotary compression element 103. That is, the first rotary compression element 102 and the second rotary compression element 103 are constituted by the intermediate partition plate 136, a cylinder 138 and a cylinder 140 arranged in left and right sides of the intermediate partition plate 136, left and right rollers 146 and 148 positioned within the left and right cylinders 138 and 140 and fitted to left and right eccentric portions 142 and 144 provided in the rotary shaft 107 with a phase difference of 180 degrees so as to eccentrically rotate, vanes (not shown) brought into contact with the left and right rollers 146 and 148 so as to respectively section inner portions of the left and right cylinders 138 and 140 into low pressure chamber sides and high pressure chamber sides, and a main frame (a left bearing) 151 and an auxiliary frame (a right bearing) 152 which close respective opening surfaces of the left and right cylinders 138 and 140 and also serving as a bearing of the rotary shaft 107.

[0102] A suction passage 153 is formed within the cylinder 138, and the suction passage 153 is communicated with a suction pipe 154 mounted to the closed container 104. The suction pipe 154 is connected to a cooler (not shown) for an artificial cooling provided within the passenger room. Further, a series of branch suction passages 156 communicated with the suction passage 153 are formed within the intermediate partition plate 136 and the cylinder 140. Further, a muffler cover 157 is mounted to the main frame 151, and a sound reduction chamber 158 suitably communicated with the inner portion of the cylinder 138 is formed within the muffler cover 157. Further, a muffler cover 159 is mounted to the auxiliary frame 152, and a sound reduction chamber 161 suitably communicated with the inner portion of the cylinder 140 is formed within the muffler cover 159.

[0103] Further, the sound reduction chamber 161 is communicated with the inner portion of the sound reduction chamber 158 by a communication passage 162 extending through the cylinders 138 and 140 and the intermediate partition plate 136, and the sound reduction chamber 158 is structured such that the external pipe 164 is connected to a discharge port (not shown) formed in the muffler cover 157. The external pipe 164 temporarily goes out of the closed container 104 from the discharge port and is communicated with the inner portion of the closed container 104 (the side of the motor element 106) from the side of the terminal 111 of the closed container 104 via a heat radiating device 175 corresponding to the heat exchanging means.

[0104] The heat radiating device 175 is mounted to a radiator (not shown) for cooling an engine corresponding to an engine cooling system provided in the vehicle, and is arranged so as to establish a heat exchange relation with the radiator. That is, the heat radiating device 175 is integrally mounted to a heat radiating fin constituting the radiator of the vehicle, and when the cooling water for cooling the engine is circulated within the radiator, the high temperature refrigerant gas passing through the heat radiating device 175 is heat exchanged with the cooling water so as to be radiated. The cooling water within the radiator is maintained at a temperature of about +80° C. equal to or less than +100° C. at which the water is not boiled, and the refrigerant gas discharged from the compression element 108 of the electric compressor having the carbon dioxide as the refrigerant becomes high temperature +230° C. over +200° C. Accordingly, the temperature difference is generated between the cooling water circulating within the radiator and the refrigerant gas passing through the inner portion of the heat radiating device 175, and the high temperature refrigerant gas passing through the inner portion of the heat radiating device 175 is heat exchanged with the cooling water so as to be heat exchanged. In this case, since it has been conventionally a well-known technique that the cooling water within the radiator is maintained at the temperature of about +80° C. equal to or less than +100° C. at which the water is not boiled.

[0105] Further, an oil pump 166 corresponding to an oil supplying means is provided at an end portion in the side of the auxiliary frame 152 of the rotary shaft 107 (an opposite side to the motor element 106), an oil suction pipe 167 provided in the oil pump 166 is provided so as to drop down in a direction of the oil storage portion 112, and a lower end thereof is open in a lower portion of the oil storage portion 112. Further, a discharge pipe 171 is mounted to an upper portion of the closed container 104 in an opposite side to the motor element 106 of the compression element 108 (in a side of the oil storage portion 112 of the cylinder 140).

[0106] Further, partition walls 172 and 173 are provided in the side of the motor element 106 and the side of the oil storage portion 112 in the compression element 108. In this case, the partition wall 172 is mounted to the muffler cover 157 or the main frame 151 (or the cylinder 138 may be employed), and sections the inner portion of the closed container 104 into the side of the motor element 106 and the side of the compression element 108 while allowing a movement of the refrigerant gas and the lubricating oil. Further, the partition wall 173 is mounted to the cylinder 140 (or the auxiliary frame 152 or the muffler cover 159 may be employed), and sections the inner portion of the closed container 104 into the side of the compression element 108 and the side of the oil storage portion 112 while allowing the movement of the refrigerant gas and the lubricating oil. Further, the discharge pipe 171 is positioned in the side of the oil storage portion 112 of the partition wall 173.

[0107] In the structure mentioned above, when an electric current is applied to a coil 128 of the motor element 106 via the terminal 111 and a wiring (not shown), the rotor 124 rotates. On the basis of the rotation, the left and right rollers 146 and 148 fitted to the left and right eccentric portions 142 and 144 integrally provided with the rotary shaft 107 eccentrically rotate within the left and right cylinders 138 and 140.

[0108] Accordingly, the refrigerant gas sucked into the suction pipe 154 from the external portion is sucked into the side of the low pressure chamber of the cylinder 138 via the suction passage 153, and sucked into the side of the lower pressure chamber of the cylinder 140 via the branch suction passage 156. The sucked low pressure refrigerant gas is compressed in accordance with operations of the roller 146, the roller 148 and the vane, respectively so as to become high temperature and high pressure and reach the sound reduction chamber 158 from the side of the high pressure chamber of the cylinder 138, thereby being discharged within the external pie 164 from the discharge port. Further, the refrigerant gas reaches the sound reduction chamber 158 from the side of the high pressure chamber of the cylinder 140 via the sound reduction chamber 161 and the communication passage 162 so as to be discharged within the external pipe 164 from the discharge port.

[0109] Further, the refrigerant gas having a high temperature and a high pressure and discharged within the external pipe 164 from the discharge port flows into the heat radiating device 175 connected to the external pipe 164 provided outside the closed container 104. The high temperature refrigerant gas flowing into the heat radiating device 175 is heat exchanged with the cooling water circulating within the radiator so as to radiate heat and be cooled, and thereafter is discharged within the closed container 104 (the side of the motor element 106). The high pressure refrigerant gas cooled and discharged within the closed container 104 reaches the side of the oil storage portion 112 within the closed container 104 while cooling the motor element 106 or the respective cylinders 138 and 140 or the like which become high temperature in the step of passing through the gap formed between the respective cylinders 138 and 140 of the compression element 108 and the partition wall 173 so as to be discharged into the external portion from the discharge pipe 171, whereby the passenger room is cooled.

[0110] Accordingly, a pressure distribution within the closed container 104 is made so that the side of the motor element 106 in the partition wall 172 has a highest high pressure HH, the intermediate partition plate 136 portion of the compression element 108 between the partition walls 172 and 173 has a middle high pressure HM lower than the above, and the side of the oil storage portion 112 of the partition wall 173 in the discharge pipe 171 has a lowest high pressure HL.

[0111] On the contrary, the oil pump 166 is rotated due to a rotation of the rotary shaft 107 so as to suck the lubricating oil within the oil storage portion 112 from the lower end opening of the oil suction pipe 167. Further, the lubricating oil is supplied to the sliding portions within the respective cylinders 138 and 140 and the sliding portions between the respective frames 151 and 152 and the rotary shaft 107 through the rotary shaft 107 so as to lubricate them.

[0112] Further, in the lubricating oil stored in the oil storage portion 112, since the pressure distribution within the closed container 104 is made so that the side of the motor element 106 in the partition wall 72 has the higher high pressure HH, the partition walls 172 and 173 have the middle high pressure HM, and the side of the oil storage portion 112 of the partition wall 173 has the lower high pressure HL, the lubricating oil can be held in the oil storage portion 112 (the side of the oil pump 106) due to the higher high pressure HH, the middle high pressure HM and the lower high pressure HL in the same manner as mentioned above. Accordingly, the lubricating oil stored in the oil storage portion 112 can be prevented from flowing out to the side of the motor element 106 by the partition walls 173 and 172. Therefore, the oil pump 166 can securely supply the lubricating oil sucked from the inner portion of the oil storage portion 12 to the cylinders 38 and 40 and the main frame (the left bearing) 51 and the auxiliary frame (the right bearing)52 serving as the bearing of the rotary shaft 7 while preventing the rotary compressor 101 from being heated.

[0113] As mentioned above, the external pipe 164 is connected to the discharge port of the compression element 108, and the heat radiating device 175 is arranged in the external pipe 164 so as to establish the heat exchange relation with the radiator for cooling the engine provided in the vehicle, it is possible to heat exchange the high temperature refrigerant gas compressed by the compression element 108 with the cooling water circulating within the radiator so as to radiate heat. Accordingly, the conventional specific heat radiating device is not required and it is possible to effectively use the engine room having the limited space.

[0114] Further, for example, in the case of employing the carbon dioxide corresponding to the natural refrigerant for the refrigerant of the electric compressor, the refrigerant gas discharged from the compression element 108 becomes high temperature in accordance with the property of the natural refrigerant. Accordingly, the temperatures of the motor element 106 and the lubricating oil are increased, however, the high temperature refrigerant gas discharged from the compression element 108 can be heat radiated at a time of passing through the inner portion of the heat radiating device 175. Further, since it is possible to radiate heat of the high temperature refrigerant gas discharged from the compression element 108 even in the case that the electric compressor is placed in the engine room or the like of the vehicle which becomes high temperature, it is possible to prevent the temperatures of the motor element 106 and the lubricating oil from being increased.

[0115] In this case, in this embodiment, the rotary compressor is employed as one embodiment of the closed type compressor, however, the structure is not limited to this, and the present invention can be effectively applied to a closed type scroll compressor comprising a pair of scrolls engaging with each other.

[0116] As described in detail above, in accordance with the invention of this case, since the structure is made such that there are provided with the electric compressor having the motor element provided within the closed container and the compression element driven by the motor element, and compressing the refrigerant gas sucked from the exterior portion of the closed container by the compression element and thereafter discharging to the external portion of the closed container, and the heat exchanging means arranged so as to establish the heat exchanging relation with the engine cooling system of the vehicle, and the refrigerant gas discharged from the compression element is flowed to the heat exchanging means, is returned to the side of the motor element within the closed container and thereafter is discharged to the external portion of the closed container, the high temperature refrigerant gas discharged from the compression element can be radiated in a process of passing through the heat exchanging means arranged so as to establish the heat exchanging relation with the engine cooling system of the vehicle. Accordingly, since it is not necessary to provide the particular radiator, it is possible to efficiently use, for example, the engine room having the limited space.

[0117] In particular, for example, in the case of using the carbon dioxide corresponding to the natural refrigerant in the electric compressor, the refrigerant gas discharged from the compression element becomes high temperature on the basis of the property of the natural refrigerant, and the temperatures of the motor element and the lubricating oil are increased, however, since the high temperature refrigerant gas discharged from the compression element can be radiated in the step of communicating through the heat exchanging means, it is possible to prevent the temperatures of the motor element and the lubricating oil from being increased. Accordingly, even in the case that the electric compressor is placed in the engine room of the vehicle or the like which becomes high temperature, it is possible to prevent the temperatures of the motor element and the lubricating oil from being increased.

[0118] Further, in addition to the items mentioned above, since the heat exchanging means is arranged so as to establish the heat exchanging relation with the radiator of the vehicle, it is possible to cool the high temperature refrigerant gas discharged from the electric compressor, for example, by the radiator for cooling the engine of the vehicle. Accordingly, it is possible to prevent the disadvantage that the compressor becomes high temperature so as to be burnt out. 

What is claimed is:
 1. A horizontal closed type compressor for vehicle use comprising: a motor element provided within a closed container so as to direct a rotary shaft in a lateral direction; a compression element driven by said motor element; a lubricating oil received in said closed container; and an oil supplying means for feeding said lubricating oil to said compression element, said oil supplying means being provided in an opposite side to said motor element of said compression element, wherein said compression element compresses the refrigerant gas sucked from an external portion of said closed container so as to discharge to the side of the motor element within said closed container, and thereafter discharges out of said closed container from the side of said oil supplying means, and partition walls sectioning an interior portion of said closed container while allowing said refrigerant gas and the lubricating oil to move are respectively provided in the side of said motor element and the side of the oil supplying means in said compression element.
 2. A horizontal closed type compressor for vehicle use as claimed in claim 1, wherein an external pipe for discharging the refrigerant gas discharged from said compression element to the side of said motor element within said closed container via an external portion of said closed container is provided in said closed container.
 3. A horizontal closed type compressor for vehicle use as claimed in claim 1 or 2, wherein said compression element is constituted by a plurality of rotary compression elements provided between both of said partition walls.
 4. A cooling system of an electric compressor for vehicle use comprising: an electric compressor having a motor element provided within a closed container and a compression element driven by said motor element, and compressing a refrigerant gas sucked from an exterior portion of said closed container by said compression element and thereafter discharging to the external portion of said closed container; and a heat exchanging means arranged so as to establish a heat exchanging relation with an engine cooling system of a vehicle, wherein the refrigerant gas discharged from said compression element is flowed to said heat exchanging means, is returned to the side of said motor element within said closed container and thereafter is discharged to the external portion of said closed container.
 5. A cooling system of an electric compressor for vehicle use as claimed in claim 4, wherein said heat exchanging means is arranged so as to establish a heat exchanging relation with a radiator of said vehicle. 